EP0564939B1 - Système de commande hydraulique pour plusieurs moteurs - Google Patents

Système de commande hydraulique pour plusieurs moteurs Download PDF

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Publication number
EP0564939B1
EP0564939B1 EP93105124A EP93105124A EP0564939B1 EP 0564939 B1 EP0564939 B1 EP 0564939B1 EP 93105124 A EP93105124 A EP 93105124A EP 93105124 A EP93105124 A EP 93105124A EP 0564939 B1 EP0564939 B1 EP 0564939B1
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EP
European Patent Office
Prior art keywords
control
pressure
control device
pump
valves
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP93105124A
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German (de)
English (en)
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EP0564939A1 (fr
Inventor
Dieter Roth
Mikko Erkkilä
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Bosch Rexroth AG
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Mannesmann Rexroth AG
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Priority claimed from DE4308004A external-priority patent/DE4308004C2/de
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Publication of EP0564939A1 publication Critical patent/EP0564939A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/47—Flow control in one direction only
    • F15B2211/473—Flow control in one direction only without restriction in the reverse direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F15B2211/50527—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves using cross-pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/51—Pressure control characterised by the positions of the valve element
    • F15B2211/511—Pressure control characterised by the positions of the valve element the positions being discrete
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5158—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/555—Pressure control for assuring a minimum pressure, e.g. by using a back pressure valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/67—Methods for controlling pilot pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators

Definitions

  • the invention relates to a hydraulic control device according to the preamble of claim 1.
  • the pressure regulator of the pump is set to a value which corresponds to the maximum permissible consumer pressure. If, for example, the consumer, such as the tilt cylinder or lift cylinder of a loader, is driven to the stop and held in this position, the pump swivels back so far and thus reduces its delivery rate to such an extent that the maximum value of the pressure set on the pressure regulator is maintained. Regardless of whether such a high pressure is required for the consumer or not in this operating state.
  • the invention is therefore based on the object of developing the known hydraulic control device according to the preamble of claim 1 in such a way that only the pump pressure occurs during operation of the hydraulic device, which is required for the function of the consumers at the time of their operation.
  • This is achieved with the characterizing features of claim 1.
  • Characterized in that the pressure setting of the pressure regulator for the pump from the control position of the control valve for the consumer with the greatest load is carried out with the actuation of the control valves at the same time a corresponding setting of the pressure regulator, which is required to actuate the consumer.
  • the control valve for the greatest load must therefore be moved in the opening direction until the pressure control device ensures a pressure build-up corresponding to the load by the pump.
  • the speed of this consumer is therefore not determined by the released opening cross section of the assigned control valve, but by the setting of the pressure control device for the variable displacement pump, which is dependent on the setting of the opening cross section of the assigned control valve. If the control pistons are in their starting position, the pressure control device is also provided no control signal is supplied to the pump. In this operating state, the pressure regulator is only acted upon by the low force of the largely relaxed control spring. The pump thus operates at the minimum delivery rate that arises against the pressure specified by the low preload of the control spring. This ensures particularly economical operation of the hydraulic system.
  • a pump is equipped with a pressure regulator, with which the pump pressure is limited to a maximum value, and with a flow regulator, which increases the flow rate by means of a control spring and the highest load pressure and can be acted upon by the pump pressure in the sense of a reduction in the delivery rate.
  • the delivery rate is adjusted so that there is a pressure difference determined by the control spring between the pump pressure and the highest load pressure.
  • the flow rate controller can be acted upon by a pilot valve of a control valve instead of the highest load pressure by means of a shuttle valve, provided the pilot pressure is higher than the highest load pressure.
  • the pilot control device can therefore only set a maximum of a value of the pump pressure which is higher than the maximum pilot pressure by the pressure difference determined by the control spring.
  • the pump pressure is therefore set either from the highest load pressure or from the pilot pressure if the highest load pressure is lower than the maximum pilot pressure, or only from the highest load pressure if this is higher than the maximum pilot pressure.
  • Figure 1 which shows a circuit diagram of a hydraulic control device for a loader, denotes 1 an adjustable pump with actuating cylinder 2.
  • 4 denotes the pressure regulator and 3 the delivery flow regulator.
  • the pressure line 5 of the pump leads to the inlet 6 of a control block 7 with three control pistons 8, 9, and 10, which, with corresponding recesses in the control block, serve directional valves for actuating the working cylinders 11, 12 for the shovel or boom, not shown.
  • the control pistons 8, 9 and 10 are connected to the connections 1 to 5 of a pilot control block 18 via control lines 13, 14, 15, 16 and 17.
  • the pilot control block has four manually operated pressure control valves 20, 21, 22 and 23.
  • a switching valve 24 which directs the control pressure set on the pressure control valve 20 up to a certain size via the control line 16 to the one control surface of the control piston 9.
  • the switching valve 24 shifts in the direction of its switching position a and interrupts the connection of the pressure control valve 20 to the control piston 9 via the control line 16. This is connected to the tank in this switching position of the switching valve 24.
  • the control line 17, which is connected to the one control side of the control piston 10, is used to shift the control pressure from the closed position shown into the floating position, in which the the work lines 30, 31 carrying the lift cylinders 12 are connected to one another and the lift cylinders can thus move freely.
  • a control line section 16a leads to a switching valve 35 which, in the switching position a, ie when pressure is applied via the pressure control valve 20 and thus also when the control piston 9 is pressurized in the “lowering” direction, the pressure line 37 of the control oil pump 38 with the control chamber 39 of a preload valve 40, which is located in the tank line 41, is subjected to control pressure.
  • control lines 13, 14, 15, 16 are operatively coupled to one another via shuttle valves 45, 46 and 47, such that the control pressure acting in the output control line 48 of the shuttle valve 47 is the highest control pressure at the pressure control valves 20, 21, 22 and 23 is set, is effective.
  • This control pressure acts on the biasing piston 50 for the control spring 51 of the pressure regulator 4 via the control line 48 and preloads the control spring 51 accordingly.
  • the highest control pressure in each case for actuating the control pistons 8, 9 is thus a measure of the pressure setting of the pressure regulator 4. If one or the other of the working cylinders 11 or 12 or both are to assume a certain working position, the pressure control valves in question will become so high Control pressure specified that such a pressure can build up in the pump line 5, which brings about a corresponding working movement of the working cylinders, the control pistons simultaneously Move 8 and / or 9 to corresponding tax positions.
  • the control piston 10 does not take part in the pressure regulation of the pump, since this is only intended to bring about a floating position.
  • the control surface of the biasing piston 50 acted upon by the control pressure is larger than the opposite control surface formed by the control piston 4a of the pressure regulator 4 and acted upon by the pump pressure. Since the forces acting on the control piston 4a result from the product of the effective pressurized area and the respective control pressure, a relatively high pump pressure can be regulated via the biasing piston with a large pressure-effective area.
  • the ratio of the control surface of the control piston of the pressure regulator acted upon by the pump pressure relates to the effective control surface of the biasing piston 50, for example, in the order of magnitude of 1 to 8 to 20. 30 bar a pressure setting of the pump in the order of magnitude up to max. Achieve 300 bar. Depending on the application, a different area ratio may also be appropriate. If high pressure is selected for control, the area ratio can also be 1: 1.
  • the exemplary embodiment according to Figure 2 differs from the exemplary embodiment according to Figure 1 only in that the highest control pressure prevailing in the control line 48 is not the pressure regulator 4 but a pressure limiting valve 60 for its respective pressure setting for the pressure regulator via the throttle 61 and the control line 62 4 acting control liquid branched from the pressure line 5 of the pump is supplied. With this arrangement, the standard pressure regulator of the pump can be retained. It is only necessary that the pressure relief valve be equipped with an appropriate pressure ratio.
  • the exemplary embodiment according to FIG. 3 corresponds to the exemplary embodiment according to FIG. 2, wherein instead of hydraulic control means, electrical control means 70, 71 in the form of control signals 70 generating electrical signals and electrical actuating magnets for the control valves 8, 9 and the pressure limiting valve 60 are provided. So this is an electrical solution.
  • control pressure for the pressure regulator is formed as throttles that can be changed with the control piston stroke in the flow cross-section by forming the interacting control edges 8, 9, 10, which control the conveying liquid circulation, to form a control block SB.
  • the greater the stroke the greater the throttling effect of the interacting control edges of the control valves and, accordingly, the pressure - seen in the direction of flow - in front of the throttles increases, the highest pressure also being determined by the control piston with the largest stroke.
  • the control liquid is withdrawn from the pressure line 5 of the pump via a throttle 61 and returned to the tank via the circulation channel 66.
  • the throttle 61 in the initial position of the directional control valves limits the maximum delivery rate to be returned from the pump to the tank via the circulation channel 66 in the control block.
  • the highest control pressure also determines the most deflected control piston.

Claims (9)

  1. Système de commande hydraulique pour l'actionnement indépendant d'au moins deux consommateurs tels que des vérins de basculement et des vérins de levage de chargeurs, la commande des consommateurs étant assurée par des valves de commande à tiroirs à positions réglables et la source de pression étant constituée d'une pompe à cylindrée variable à dispositif de régulation de la pression, le signal d'excitation des valves de commande pouvant simultanément être asservi au dispositif de régulation de la pression, caractérisé en ce que le réglage de la pression du dispositif de régulation de la pression (4) provient exclusivement du signal de pilotage du tiroir de commande qui commande le consommateur avec la plus grande charge.
  2. Système de commande hydraulique selon la revendication 1, caractérisé en ce que l'excitation des tiroirs de commande des valves de commande vers la position de commande respective se fait au moyen de la pression de commande réglable, que la pression de commande respective la plus élevée (20, 21, 22, 23) qui alimente l'une des valves de commande (8, 9) pour son déplacement constitue simultanément un paramètre de réglage de la pression du dispositif de régulation de la pression (3) pour la pompe à cylindrée variable (1).
  3. Système de commande hydraulique selon la revendication 1 ou 2, caractérisé en ce que le dispositif de régulation de la pression est constitué d'un régulateur de pression (4), lequel est alimenté par la pression de la pompe lors d'un plus petit débit de la pompe (1) et, lors d'un plus grand débit, par la pression de commande respectivement la plus élevée (20 à 23) pour l'excitation des valves de commande (8, 9).
  4. Système de commande hydraulique selon la revendication 3, caractérisé en ce que le ressort de régulation (51) du régulateur de pression (4) prend appui sur un piston de prétension (50) qui est alimenté par la pression de commande respectivement la plus élevée pour l'excitation des valves de commande et par le fait que le ressort de régulation est prétendu en conséquence par ce piston de prétension.
  5. Système de commande hydraulique selon la revendication 4, caractérisé en ce que la surface alimentée en pression du piston de prétension est supérieure ou identique à la surface alimentée en pression du tiroir de régulation (4a) du régulateur de pression (4).
  6. Système de commande hydraulique selon la revendication 1 ou 2, caractérisé en ce que le dispositif de régulation de la pression consiste en un régulateur de pression (4) dont le réglage de la pression est assuré par une pression de commande hydraulique dont la grandeur est définie par une valve de pression (60) et dont le réglage dépend de la position de commande du tiroir de commande de la valve de commande (8, 9) qui commande le consommateur (11, 12) avec la plus grande charge.
  7. Système de commande hydraulique selon la revendication 2 ou 6, caractérisé en ce que le réglage de la valve de pression (60) se fait par la pression de commande la plus élevée pour l'excitation des valves de commande (8, 9) et que le fluide de commande est prélevé en passant par un étrangleur (61) du côté pression (5) de la pompe (1).
  8. Système de commande hydraulique selon les revendications 1 et 6, caractérisé en ce que l'excitation des tiroirs de commande se fait par des moyens de commande électriques (70, 71), le courant de commande le plus élevé constituant simultanément un paramètre pour la valve de pression (60) également réglable par des moyens de commande électriques.
  9. Système de commande hydraulique selon la revendication 1, caractérisé en ce que les valves de commande consistent en des distributeurs à 6 voies à canal de recirculation, que le dispositif de régulation de la pression consiste en un régulateur de pression (4) dont le réglage de la pression se fait par la pression du fluide de commande qui est dérivé de la conduite de la pompe (5) en passant par un étrangleur (61) puis redirigé vers le réservoir en passant par le canal de recirculation (66) devant être étranglé par les valves de commande (8, 9, 10), l'importance de la pression étant déterminée par la valve de commande exécutant la plus grande course et présentant donc la plus petite section d'étranglement pour le fluide de commande réaffluant dans le réservoir.
EP93105124A 1992-04-04 1993-03-29 Système de commande hydraulique pour plusieurs moteurs Expired - Lifetime EP0564939B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4211314 1992-04-04
DE4211314 1992-04-04
DE4308004A DE4308004C2 (de) 1992-04-04 1993-03-13 Hydraulische Steuereinrichtung für mehrere Verbraucher
DE4308004 1993-03-13

Publications (2)

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EP0564939A1 EP0564939A1 (fr) 1993-10-13
EP0564939B1 true EP0564939B1 (fr) 1995-12-13

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EP (1) EP0564939B1 (fr)
JP (1) JPH0674204A (fr)

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DE10331533B4 (de) * 2003-07-11 2005-11-03 Brueninghaus Hydromatik Gmbh Steuer- und Stellsystem für ein Hub- und Kippwerk eines Arbeitswerkzeugs in einer mobilen Arbeitsmaschine

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US5873244A (en) * 1997-11-21 1999-02-23 Caterpillar Inc. Positive flow control system
US6092454A (en) * 1998-07-23 2000-07-25 Caterpillar Inc. Controlled float circuit for an actuator
WO2000032970A1 (fr) * 1998-12-01 2000-06-08 Hitachi Construction Machinery Co., Ltd. Vanne de commande
US6264431B1 (en) * 1999-05-17 2001-07-24 Franklin Electric Co., Inc. Variable-speed motor drive controller for a pump-motor assembly
US6644335B2 (en) * 2000-12-15 2003-11-11 Caterpillar S.A.R.L. Precision orificing for pilot operated control valves
US20020112475A1 (en) * 2001-02-07 2002-08-22 Michael Cannestra Method and apparatus for controlling fluid pressure in a hydraulically-actuated device
JP2006220177A (ja) * 2005-02-08 2006-08-24 Komatsu Ltd 油圧ショベル
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WO2011143301A1 (fr) 2010-05-11 2011-11-17 Parker-Hannifin Corporation Système hydraulique compensé en pression avec régulation différentielle de la pression
AU2011353519B2 (en) * 2011-01-04 2015-09-10 Crown Equipment Corporation Materials handling vehicle having a manifold located on a power unit for maintaining fluid pressure at an output port at a commanded pressure corresponding to an auxiliary device operating pressure
US9347200B2 (en) * 2012-06-04 2016-05-24 Cnh Industrial America Llc Fluid control system for work vehicle
WO2014127356A1 (fr) * 2013-02-15 2014-08-21 Parker-Hannifin Corporation Système hybride à centre ouvert sensible à une charge variable
DE102015218832A1 (de) * 2015-09-30 2017-03-30 Robert Bosch Gmbh Pumpen-Regler-Kombination mit Leistungsbegrenzung
CN106286435A (zh) * 2016-08-30 2017-01-04 力源液压（苏州）有限公司 一种数字式变量柱塞泵及控制方法

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WO2005028879A1 (fr) 2003-09-17 2005-03-31 Brueninghaus Hydromatik Gmbh Systeme de commande et de reglage hydraulique a compensation de volume

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US5528911A (en) 1996-06-25
EP0564939A1 (fr) 1993-10-13
JPH0674204A (ja) 1994-03-15

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